Swinging plate valve construction



June 7, 1960 J. w. BROOME swmcmc: PLATE VALVE CONSTRUCTION 4 Sheets-Sheet 1 Filed May 1'7, 1957 R O T N E V m Joseph WBroome BY WM June 7, 1960 J. w. BROOME 2,939,483

SWINGING PLATE VALVE CONSTRUCTION Filed May 17, 1957 4 Sheets-Sheet 2 1:1. 5. 3' V.

54 5 ii i 5 u unu 'Jbseph/ .Broome June 7, 1960 J. w. BROOME ,93

swmcmc PLATE VALVE CONSTRUCTION Filed May 17, 1957 4 Sheets-Sheet 3 66 INVENTOR Joseph Wfu'oome ATTORNEYS 2,93 9,483 Patented J one 7',- 196i):

2,939,453 3 SWINGING PLATE VAYZVE CONSTRUCTION Joseph W. Brdomeiflorth Sudbupy; Mass, assignor to The Oilgea'r Company, Milwaukee, Wis. Filed May 17; 1957', see No; 659,856

22 I Claims. (G l. 137 622) V This invention relates to .animproved valve construction. Valves made according to my invention may be utilized to advantage inservomechanisms; they are also or" particular utility in applications.requiring .the control of flow ofcorrosive and erosive fluids. My invention relates to an essentially frictionlessvalve of the swing plate type having power handling. capabilities-.-

Many automatic control systems-,eg. 'servomechanisms, employ hydraulic pumps and, hydraulic motors- These motors may operate in rotation or translation to drivetheir loads and may be constructed in any of several well-known formseg. vane and piston-cylinder arrangements. Frequently the: output ofthe motor, i.e. its position or speed, is controlled .by avalvewhich regulates the flow of hydraulic fluidv to it. These valvesare generally actuated in accordancewitherror signals in the form. of electrical voltages or currentskdeveloped by comparing the output performance witha-a commandsignal.

They may boot the so-cal-led three-way or four-way type depending upon the application; A.fourwayvalve: has

the two hydraulic power outputs connected. to the motor,-

the valve serving to switchthe-incoming hydraulic stream to one or the other of the outputs. towdetermine the direotion inwhich hydraulic-force is to be applied to' the motor. Three-Way valves; on the, other-hand have but one control line connected to themotor' andthus are adapted to drive the motor inbut one direction the force required to return thernotor being supplied. by a spring, gravity, or other appropriate means;

Tobe efliciently employed servo systems; these valves should be capable of controlling'l'arge hydraulic power in response to a minimum ,tinput 'signal additionally' they should becapablelof :fias't response to: an'i nput. signal. The: power outpufi is proportional tonthefaptoduct:

ing therethrough. Thus, to controllarge' loads, devalue-r must withstand high pressures, andt, provide; .upor'r. actuation, valving orifices of sufiicient: area to permitithe' de'-" sired relatively large flow: In: generah. higher pressures requiring lower flow rates are; .d'esirable-.in order tormini mize the. size of the systemtcomponentsa Moreovenwhight" erpressure requires: less: motionv of: that moving parts of such factors as inertia valv'e friction; hydr auli'c pressure; and flow rate. Of't-liese -factorsinertia i's 'minimized by keeping the mass of the moving parts low; and the effects of pressure andflow maybe compensated for by proper shaping of the valve; chambers. Friction on the other hand has been a serious probl'em-incommercially prae ticablevalves. It degrades both th'e' linearity of tli'e orifice area--actuating forcecurve and the sensitivity of such va'lves Prior to my invention the" hydraulic sp'ool -typejservo' It consists of acylinder valve was most widely used;

.. States Patent Cfice the lands thereon from the cylinder lands to form orifices through. which the valvedfitiid flows. Such. orifices: al-' low the hydraulic fluid to pass through various. eli'am-v hers in. the valve between a hydraulic pump andv anhydraulic motor. Valves of this .typeare costly to manufacture, particularly since they require close-tolerance. machining of the interior portions of a diameter cylinder. Moreover, they are subject to frictional forces between' the spooland cylinder. Further, minute. solid particles carried in the hydraulic stream t'end 'to lodge between the moving and stationary-members. of the valves, increasing friction and causing sticking. These particles thus increase valve hysteresis; they increase the actuating. force required for a measurable change in. flow rate, and they make it diflicult for the valve to' reach the null position, i.e. position of flow, because the restoring force is least. at this point. Therefore successful spool; type' valves are frequently driven byhydrait lic actuators in turn controlled by torque motors instead. of directly by the torque motors themselves. This increases the response time of the systems and alsointro herent in the spool valve.

duces additional non-'linearities tending toward system in'-' stability."

The suspended plate valve appeared in tin attempt to eliminate some of these undesirable: characteristics 'inconfiguration similar to that of the spool type, except that: the lands and chambers are formed with flat rather than cylindricalsurfaces. A valve plate" having lands and chambers cooperating with those of a stationary valve block may be made to move over the block in its val ving-function-with minimum" friction principally because of the separation of plate and block. caused by the pressure of the fluid therebetween. Prior to my invention this pressure was counteracted by the compression ofsupport members" from" which the plate was suspend ed. To prevent buckling of these members, they should be relat'ively thick, thus making-"deflect ion thereof and translation of the valve plate difficult The flow rate which may be obtained practicably by' such a valve'urider high pressure is therefore low, as is the resultant power handling capability. Suspended plate valves of this do si'g'n also' tend to" catchs'usp'endedparticles between pl'ate and'block to such degree that sticking; with its attendant elfe'cts,is' ai serious-problem.

As will be seen hereinafter, there are many other ap pli'cations' in addition to servoniechanismsinwhich valves" made according to my invention may be rea'dily utilized. Inmany cases it is desirable to control flowof hot gases under high pressure. Prior to my invention the erosive actions of such gases caused inordinate wear on valves" usedfor such control. Moreover, a serious problem is enco'unt'er e'd in maintaining sufficiently tight seals-forsuclr gases while retaining relative ease" of valve control.

It is often desirable to control the flow of a slurry containing suspended particles ofvariou's sizes; Vfith prior valves theincreased friction caused by such par ticles often prevented suflicient closure.

Accordingly, it is an object of my invention to provide an improved valve having a minimum of friction between" moving and stationary parts. It is another object of my invention to provide. a valve of the above character whose operation is substantially unalfected by particles suspended in the valved fluid. It is a further object of my inven-. tion to provide a valve of the above character having .a large powerhandling capability. Yet another object oi It may have. a mechanical my invention is to provide a valve of the above character requiring a minimum actuating force. It is a still further object of my invention to provide a valve of the above character which resists corrosion and erosion by the valved fluid. Yet another object is to provide an. improved valve assembly incorporating a valve of the above character. It is a further object of my invention to provide a valve of the above character capable of eflicient useas a controlling element in hydraulic servo systems. Another-object of my invention is to provide a valve of the above character which is relativelylow in cost and simple to manufacture. A final stated object of my invention is to provide valves of the above character adapted for either three or four-way operation. Other objects of my invention will in part be obvious and will in part appear hereinafter.

The invention accordingly comprises the features of construction, combinations of elements, and arrangements of parts which will be exemplified in the constructions hereinafter set forth, and the scope of the invention will be indicated in the claims.

For a fuller understanding of the nature and objects of the invention, reference may be had to the following detailed description taken in connection with the accompanying drawings in which:

Figure 1 is a schematic representation of my four-way valve and associated components as connected for use in a typical servo system,

Figure 2 is a side elevational view, partly in section, of a four-way valve made according to my invention showing its mounting within the valve housing,

Figure 3 is a top plan view, partly in section, taken along the line 33 of Figure 2,

Figure 4 is a vertical sectional view taken line 4-4 of Figure 3,

Figure 5 is a fragmentary vertical sectional view of a four-way valve taken along the line 5-5 of Figure 4,

Figure 6 is a view of the above block taken along the line 66 ofFigure 4,

Figure 7 is a vertical sectional view similar to Figure 4 and depicting a three-way valve which is a second embodiment of my invention,

Figure 8 is an enlarged fragmentary vertical sectional view similar to Figure 4 and showing a third embodiment of my invention including a pressure compensating structure, and

Figure 9 is a fragmentary sectional view taken along line 9-9 of Figure 8.

Referring to Figure 1, my four-way swing plate valve may have a valve plate 2 for movement over a valve block-generally indicated at 4 in response to the motion of a torque or force motor 6 transmitted to the plate through suitable linkage generally indicated at 8. The valve is connected to regulate the flow of hydraulic fluid from a pump 10 to a hydraulic motor '12. Thus fluid from the pump enters a pressure chamber 14 byway of a line 15 and passes into a chamber 16 in plate 2 bounded along the by lands 18 and 19. With the plate in the full line position of Figure 1, land 18 engages a land 20 in block 4 to prevent flow in that direction. Land 19 is thus disengaged from land 21 permitting fluid to pass from chamber 16 into a control chamber 22 in block 4 and thence to the motor 12 through a line 24. It leaves the motor to return to a second control chamber'26 in the block through a line 28. The flow continues into an exhaust chamber bounded by lands 18 and 32 through an orifice formed by the disengagement of land 18 from a block land 33. It may then return to the pump 10 through an exhaust chamber 34 and a line 36. Accordingly the flow is to the motor 12 through line 24 and to exhaust through line 28.

The flow to motor 12 may be halted by energizing the torque motor 6 to move valve plate 2 to the left (Figure 1) to the dotted line null or center position. Lands 18 and 19 then block chambers 22 and 26 from pressure 4 chamber 14. Further leftward movement of the valve plate will cause reversal of the direction of flow to the motor 12. Land 18 will then be disengaged from land 20 to allow communication between chambers 14 and 26 through chamber 16, and lands 19 and 21 will be engaged to prevent flow to chamber 22. Engagement of lands 18 and 33 will cut off chamber 26 from chamber 30; and disengagement of land 19 from a block land 37 will permit flow between chamber 22 and an exhaust chamber 38 by way of a chamber 40 in plate 2 bounded by lands 19 and. 42; The fluid then returns to the pump 10 through a line 44. -Accordingly,-the flow is to motor 12 through line 28 and from the motor to exhaust through line 24.

. The direction of motion of the hydraulic motor 12 may thus be changed at will by moving the valve plate 2 over the block 4 in response to appropriate input signals to the torque motor 6. The mode of operation of all fourway valves of the sliding plate type is similar to that described above, although the particular land-chamber configuration thereof may vary.

Prior to my invention the sliding plates of these valves were supported by depending resilient members acting in compression against the hydraulic forces in chambers 14, 22, and 26. Compression of these members caused by such forces aids in providing clearance between'the plate and block to eliminate friction therebetween, the supporting members bending upon the actuation of the valve to act like hinges for the plate. To prevent buckling under pressures of upwards of a thousand p.s.i. or more, these members must have substantial cross sectional areas. However, when they are so heavily constructed it is difficult to deflect them even the few thousandths of an inch necessary to operate this type of valve. The available power output, as well as the power gain, is insufficient for normal operation as a direct controller.

The present invention overcomes this problem by supporting the valve plate from members or supports which are in tension and thus are not subject to buckling. These supports may be much thinner than the compression members formerly used; and thus they are relatively easily deflected for plate movement upon actuation of the valve. Since the valve plate may thus undergo greater excursions with less actuating force, the available flow rate is materially increased as are the power handling capabilities and power gain of the valve. My valve has other advantages which will be described, e.g. its operation may be made relatively independent of particles suspended in the fluid passing through it and it has improved stability in the null position.

More particularly, as seen in Figure 2, my valve assembly may include a base 46 and a housing 48 suitably secured thereto. As seen in Figures 2 and 3, a pair of foot blocks 50 and 52 are rigidly secured to opposite sides of the valve block 4 in any suitable manner such as brazing or welding and fastened to the base 46 by suitable screws 54. The valve plate 2 is supported above the valve block by a pair of supports 56 and 58. These supports are preferably thin sheets of steel welded at their upper ends to a pair of brackets 57 and 59 which are suitably secured to the top of plate 2 as by screws 61. The lower ends of the supports may be secured to a pair of foot blocks 60 and 62 affixed to the base 46 by screws 64. Thus the plate 2 is supported above the block 4, and there is a slight clearance between the opposing faces of these parts to eliminate friction upon movement of the plate. This clearance is exaggerated in the drawings for purposes of illustration. Further, the supports act as leaf springs tending to restore the valve plate 2 to the center or null position upon deflection notshown) suitably attached tothebase 46}. The ex hattst chambers 34-and 38-preferably extend across the valve block 4 in similar fashion. The upper face of the valve block 4 is preferably as- Hat and smooth as practicable;

Theval've plate 2 has its lands and chambers arranged to cooperate with those-of the block 4. Thus the chambers 16, 30, and 40 and lands 18- and 19 extend crosswise of the plate which preferably is the same width as the block 4. Accordingly, the chambers and lands in the plate and block are preferably coextensive and exactly opposed when'the valve is in its center or null position.

More particularly, lands 18 and 19- are positioned to block the chambers 22 and 26 when the plate is in the null position as can be seen in Figure 4. In such position exhaust chambers 30 and 40 are directly opposite chambers 34 and 38. Thus upon the-slightest movement of thev-alve plate 2 by torque motor 6, an orifice connect's chamber 16 to either control chamber 22 or 26. Theother control chamber not so connected wi-llbe connected with its adjacent exhaust chamber. As will be described, the lands 18 and 19 may overlap or underlap, -i.e.,- extend beyond or not quite cover, their corresponding control chambers, depending on the valve applications. Plate 2 may be secured to the linkage 8 extending. therethrough by a nut 72 (Figure 4) and to the torque motor 6 by a nut 73. The torque motor in turn may be mounted in suitable fashion upon a standard 74 secured' to b as'e-46. e

To prevent unwanted venting of fluid from the valve, the ends of chambers 14, 16, 22', and 26 are sealed with covenplates 76; 78, 80, and 82. As shown in Figures 2 and '5,- these plates may be brazed, welded, or otherwise suitably secured to the sides of plate 2 and block 4; The

upper edg'es of cover plates- 80 and S2 and the lower" edges: ofi plat'es 76- and78 are preferably coextensive withthe upper face of block. 4 and the lower face of the plate 2", respectively; ltzwilli be noted th at'they do not cover the endsof'the exhaust chambers 30, 34; 38, and 41 Thus these chambers are vented directly to" the exterior of the valve, and the. fluidl entering them from chambers 22; and 26 encounters essentially no backpressure. The fluid issuing; from the exhaust-chambers may thus be retaine'drwithin the housingx48 and then. withdrawn to a sump and pump for recirculation in a well known man ner.

As bestseen in Figure 3, torque motor 6 may have an armature 81-. conventionally mounted for motion. between apair of pole pieces 83 under: the influence of amagne'tic fieldldeveloped by electrical coils (not shown). Thus the armature may stroke valve plate 2 through its connection to" linkage 8' at the nut 73; Since, as pointed out" above; the valve plate supports 56 d. 58. gervei'a re:-

storing; springs; no further springs for this purpolsear'ef It will be understoodrequired in the torque motor 6'. that. for high power applications Where the-actuating force of a: torque or force. motor. is insufiicient for efiicient-"oporation, a hydraulic actuator may be used to stroke the valveplate-Z;

Referring again to-Figure 4', the fluid: from: apump' or other. pressure source enters the pressure chamber 14 through passage '66 and then is conducted by chamber" 16 to one of the control chambers 22" or 26 depending onthe direction oi, actuation of torque motor 6 (Figure 2) and consequent position of plate 2. The fluid from this chamber travels to thehydraulic motor and thenireturns to the other control chamber from which it passes into an exhaust chamber to be ventedto the exterior." of the valve, as previously described with reference to Figure 1. The flow of fluid through. the valve substantially ceases when the valve plate 2 returns to the null position;isupports 56 and SS' are continually urging the plate toward this position. Reversal of flow may be achieved byfyontinfiing movement of plate 2 beyondthe. nulllpo! between the valve plate and block may" be required to" For ellicient operation in servo systems',=the outercor ners of the lands and chambers shouldbe as square possibleto linearize valve characteristics. Moreover, the areas formed between the lands in the valveplate 2 andblock 4 for fluid flow are nearly proportional to the valve plate displacement to either open position. Thusthe flow rate may be made a substantially linear function of valve displacement, an important feature inservo systerns.

Further, the orifices extend across the entire width. of the valve, and therefore, for a given displacement of the valve plate there is a correspondingly large change in orifice area than with the configurations of prior valves; this makes possible a substantial increase inpower gain. Further, as pointed out above, the supports 56"and' 58, being in tension, may be madefrom relatively thin stock andthus are readily deflected by the valve actuator; Con-- sequently, this valve is capable oi? a high power output with a lower actuating force.

The clearance between the valve plate 2 and block 4 may vary depending upon the particular application. For example, in hydraulic servo systems it may run from .0002 inch to .003 inch depending upon the particular fluid, the size of suspended particles, etc. It will be noted that the clearance may be adjusted after machining of the cooperating faces of the valve plate and block. Thus if there is insufficient clearance, the bottom of the block may be ground to lower the upper surface thereof, and if it is too great the bottoms of the supports 56 and 58 and the blocks and 52 attached thereto may be ground to lower the bottom surface of plate 2.

The extent of overlapping of the chambers 22 and 26 by' lands 18 and 20 also depends upon the application of the valve. An exact match, i.e., zerooverlap and zero underlap, may be desirable in many servo applications. Where the valve isto control the flow of gases, a substantial overlap, togetherwith a 'minimum clearance provide an effective seal in thenullposition. On the other hand where slurriescarrying solid particles" of considerable sizeare to be valved, it may be desirable to have a certain amount of underlaptogether with greater clearance between plate and block to prevent sticking and also to minimize the valve dead band, he, the: amount of valve plate movement fromthe null to' theopen position; I

It will also be seen that the materials forming. the valve plate and block may vary depending upon the valve application, Thus aluminum may be satisfactory at low pressures while higher pressures may require a stronger material such as steel. Where corrosive fluids are to be va'lve'd, the portions of the valve exposed thereto may be coated with a non-corrodingsubstance orthe valve plate and block may be made of such material. When the flow of hot erosive gases is to be controlled, the plate and block may be molded of or glazed with ceramic material resistive to such wear. In-prior valve constructions the use of such materials was practically impossible because of the difficulty of machining them to the required configurations. The present valve may in many cases be fabricated without final machining operations. Where extremely close-tolerances are required, the configurations of the parts readily permit grinding for shaping or even hardened ceramics.

The operation of the present valve is relatively independent of particles suspended in the valved fluid because the plate supports 56 and 58 act in tension. Such particles have hindered proper operation of prior valves by lodging between the surfaces of the moving and sta tionary parts to cause sticking, or friction therebetween. This can be particularly troublesome when it is attempted to return the valve to the center or null position; In such. case the signal may be applied to thevalve actue ator at a minimum. level, and the restoringforcemay ment of the parts thus inhibits sticking, and the valve.

returns to the null or dead center with minimum applied force.

The present valve has inherent stability in the null position markedly exceeding anything achieved by sliding plate valves using compressional valve plate supports. The pressure in the various chambers, particularly that in chamber 16 which is continuous during operation, pushes the plate 2 away from the block, tending to increase the clearance therebetween. As it is furthest from the block in the null position, this pressure constantly urges the plate to remain in that position. With compressional supports the reverse is true, i.e., the clearance is greater away from the null position with the fluid tending to displace the plate slightly to either side thereof. Resulting instability may cause drift of the hydraulic motor and oscillatory conditions in the entire system.

In certain applications the pressure supplied to chambers 16, 14, 22, and 26 may be high enough to bow the central portion of the plate upwardly, increasing substantially the plate block clearance and hindering effective control. In Figures 8 and 9 there is illustrated a modification of my valve to be used with such high pressure ranges. As shown therein, a pair of blocks 84 and 86 may be suitably secured to the sides of the valve block 4 to seal chambers 14, 22, and 26 in the manner of cover plates 80 and 82 of Figure 5. Bolts-88, threaded into blocks 84 and 86, extend through a yoke generally indicate at 90 extending over the top of plate 2. Yoke 90 includes vertical flanges 92and 94 extending therefrom and a top 96; these flanges are spaced from plate 2 and plates 76 and 78, and the top is spaced from plate 2 as indicated at 9611 (Figure 9). It will be understood that some of these space dimensions are exaggerated in the drawings in the interest of greater clarity. The valve plate may have a pair of chambers 98 and 100 opening toward the bottom surface of yoke 90 and connected to chamber 16 by passages 102 and 104. Thus in operation chambers 98 and 100 are under the same pressure as that in chamber 16, i.e., the output pressure of pump (Figure 1). Ward (Figure 8) force in chambers 98 and 100 to offset the upward bowing force. It will be apparent that the areas of chambers 98 and 100 may be set to balance out part or all of the upward (Figures 8 and 9) forces in chambers 16, 22, and 26 depending upon the results desired in a particular application.

There may be some leakage of fluid between plate 2 and yoke 90. However this flow comes directly from the pressure source via chambers 14 and 16 and therefore it will not efiect valve operation. Thus the valve plate 2 may be of relatively thin light material with low inertia and yet maintain proper spacing from block 4 for efficient operation.

In Figure 7 I have illustrated a three-way valve made according to my invention. As shown therein the valve has a cooperating valve plate 106 and valve block 108, the valve block being suitably secured to a base 110 by supports 112 and 114 secured thereto. Supports 112 and 114 are secured to the base by blocks 116 and 118 and bolts 120 extending therethrough. Suitable linkage generally indicated at 122 may be provided to connect the valve plate to a motor such as motor 6 (Figure This pressure exerts a down-' 1) Thus plate 106 may move over block 108 to regulate the flow of fluid through the valve in the manner described above.

More particularly, block 108 has a pressure chamber 124, a control chamber 126, and an exhaust chamber 128. Valve plate 106 has a chamber bounded by lands 132 and 134 and an exhaust chamber 136 bounded by lands 134 and 138. Passage 140 is connected to the pressure source such as the pump 10 (Figure 1). In the null position land 134 is positioned to block control chamber 126 with overlap or underlap as desired. When valve plate 106 is deflected to the right, pressure chamber 124 is connected to control chamber 126 via chamber 130. The fluid then passes through a passage 142 to a hydraulic motor (not shown). This motor may take the form of a piston and cylinder with restraining spring, etc., working against the force of the incoming fluid. When plate 106 is moved to the left back to the null position with land 134 blocking chamber 126, further flow is prevented and the motor remains substantially locked as previously set. Upon further valve movement to the left, control chamber 126 is connected to exhaust chambers 128 and 136, and fluid from the motor will be vented therethrough. Accordingly the compressed spring in the manner and of the same materials, and further in highpressure systems it may be used with a pressure compensating system similar to that of Figures 8 and 9.

Thus I have described an improved valve construction which may be usefully employed in controlling fluids of various kinds including gasses and slurries. The valve has particular application in servo systems where it has the advantages of essentially frictionless operation, freedom from sticking, and inherent stability. Moreover, it is capable of high power output with comparatively low actuating force. My valve may be manufactured by well-known techniques and may be adjusted after initial machining to minimize the reject rate.

I have described both a three-way and a four-way valve and a pressure compensating arrangement which may be'used with'either valve. As noted, these valves may be made from a wide variety of materials depending upon application. While I have particularly described certain land and groove configurations, it will be understood that other configurations may be incorporated into these valves without departing from the scope of my invention. Moreover, it will be apparent that the plate supports and cooperating faces of the plate and block may, within the scope of my invention, take other forms than those specifically described above. Also, the movement of the plate may be rotary rather than translational, depending upon the particular forms employed.

It will thus be seen that the objects set forth above, among those made apparent from the preceding description, are efl'iciently attained and, 'since certain changes may be made in the above constructions without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

It is also to be understood that the following claims are intended to cover all of the generic and specific features of the invention herein described, and all statements of the scope of the invention which, as a matter of language, might be said to fall therebetween.

I claim:

1. In a valve construction, the combination of a valve block, a plate associated with said block, said plate and block having opposing surfaces with valve chambers formed therein, said chambers being so shaped as to control fluid under pressure upon relative movement of stresses said surfaces substantially along each other, a member interconnected with said blockand adapted to urge said plate against said block: substantially only under tension, said tensionally acting member being adapted to yield to permit said relative movement of said surfaces and being substantially non-extensible in a direction coinciding with that of said tension.

2'. A valve of the-flat face type for controlling the flow offl-uid under pressure, said valve comprising members with opposed faces having lands. and chamber portions and single supporting means rigidly connected to one of said members and rigidly connected to the other of said members, said means being nonextensible and subject substantially only to tension'by the pressure of said fluid tending to separate said members, said supporting means being; adapted to yieldtopermit said members to move relative to each other, thereby to control the flow of said fluid.

3 The combination defined in claim 2 including resilient means-opposing said yielding of said supporting means.

4. A valve for receivingfluid under pressure, comprising members" withopposed faceshaving land and chamber portions cooperating to" controlfluid flow, relative movement of said faces along each other controlling said flow, meansfor admitting saidfluid into at least one of said chamber portions whereby said pressure of said fluid tends to separate said members, means supporting one of said-'members'for movement of its said face along the face of theother said member, said supporting meansacting only in tension in a' direction" transversely of said faces and. being non-extensible in suchtransverse direction and being resilient in a direction parallel to said faces.

5. Ina valveflconstruction the combination of a valve block, a platev associated, with said? block, said plate and block: having; cooperating faces so shaped as to control a ainst said pressure and being resilient in the 'direction of movement of said plate and'ther'eby beingadapted tourge said plate to its initial position upon movement said plate'and block, whereby pressure-of said fluid may urge the plate and block apart, a plurality of valve plate' I supporting members, means securing each of said mern:

fluid; under, pressure upon relative: movement thereof along: each. other,,a member supportingsaid plate in closely spaced relationship with said block-,means securing one' end of said member ,to said plate,.andmeans securing the: other end. thereof to said block; said member? being. adapted to act only in tension against' sai'd pressure and further adapted to yield in a direction permitting said relative movement of said cooperating faces.

6. The combination defined in claim 5 in which said member is resilient in the direction of said relative movement.

7. In a valve construction, the combination of a valve block, a valve plate disposed with a face thereof closely spaced from a cooperating face of said block, a cooperating land and groove in said faces adapted to valve a fluid upon relative movement of one face along the other, means adapted to introduce said fluid between said plate and block, whereby pressure of said fluid may urge said plate and block apart, means supporting said valve plate adapted to act only in tension against said pressure, and means securing said supporting means to said plate and block for movement therewith, said supporting means being also adapted to yield to permit said relative movement of said faces.

8. The combination defined in claim 7 in which one end of said supporting means moves relative to the other end thereof upon relative movement of said faces.

9. In a valve construction, the combination of a valve block, a valve plate disposed with a face thereof closely spaced from a face of said block, means supporting said plate for movement along said block, means securing said supporting means to said plate and block, a cooperating land and chamber arrangement in said plate and block adapted to valve a fluid upon said movement of said plate, means adapted to introduce said fluid between said plate and block, whereby pressure of said fluid may urge them apart, said supporting means acting only in tension bers to said plate and said block; whereby said members act only in tension against said pressure, said members being resiliently deflectable, whereby'said face of said face of said block tovalve said fluid.

11.- in a valveconstruction, thecombination of a valve plate may be resiliently moved substantially along said" block, a valve plate disposed-with a first face thereof closely spaced from a second face of said block, a pres sure chamber in said second face and a pair of control chambers therein on opposite sides of said pressure chamber, means forming passagesiconnecting said chambers withthe exterior of said block, a pair of lands on said first surface positioned and adapted substantially to block said control chambers when the valve is in'the nullpo'sition, chamber'in' said second surface bounded by land'sand-"communicating with said pressure" chamber, valve plate supports, means for securing said supports to said plateand said block, wherebysa'id supports'may act only in" tension against force'exerted bysai'd fluid tending toseparate said plate and block, relative translation of said first face along said secondface and away from said null positionperinitting' fluid to flow through" said pres sure' charnber and'said chamber in saidjplate and into a control chamber to eife'ct the valving actionof said valve;

12'. The combination defiried in claim"11 in which said. supports are resilient in". the direction of relative translation of said "valve plate, whereby upon translation away from said null position the ends of said supports" securecllto' said plate are deflected with respect to the ends thereof secured to' said block, said deflection causing a force to be exerted by said supports on said plate and block tending to restore them to the null position.

13. The combination defined in claim 11 in which. said chambers are substantially in the form of rectangularslots extending across said block and plate at right angles: to the direction of relative motion thereof, and includ-- ing means sealing the ends of said chambers to prevent the flow of the valved fluid therefrom.

14. The combination defined in claim 11 including a pair of exhaust chambers in said plate bounded on one side by said lands, said lands being substantially coexten-- sive with their corresponding control chambers, whereby upon relative translation of said plate away from said null position one of said control chambers may com-- municate with said chamber in said valve plate and the other control chamber may communicate with its adjacent exhaust chamber.

15. In a valve construction, the combination of a valve block, a valve plate disposed with a first face thereof closely spaced from and substantially parallel to a second face of said block, a pressure chamber in said second face, means forming a passage between said pressure chamber and the exterior of said block, a control chamber in said block, means forming a passage connecting said control chamber with the exterior of said block, a land in said first face opposite said control chamber and substantially coinciding with the opening thereof in said second surface, means forming a connecting chamber in said valve plate bounded on one side by said land and communicating with said pressure chamber, valve plate supports s ecured to said valve plate and said valve block, whereby 11' said supports may act only 'in tension against force of the valved fluid tending to separate said plate and said block.

16. The combination defined in claim 15 in which, upon translation of said valve plate with respect to said block to valve said fluid, the ends of said supports secured to said plate are deflected with respect to the ends secured to said block, said supporting members bein resilientsin the direction of said translation.

17. The combination defined in claim 15 in which said chambers are in the form of rectangular slots extendingacross said plate and block and substantially at right angles to the direction of said translation, and which includes means sealing the ends of said chambers to prevent escape of the valved fluid therefrom.

18. The combination defined in claim 15 including an exhaust chamber in said plate bounded on one side by said land.

19. In a valve construction, the combination of a valve block, a valve plate disposed with a first face thereon closely spaced from a second face on said block, a pressure chamber in said second face and a pair of control chambers therein on opposite sides of said pressure chamber, means forming passages connecting said chambers to the exterior of said block, a pair of lands on said first face positioned and adapted substantially to block said control chambers when the valve is in the null position, a chamber in said first face bounded by said lands and communicating with said pressure chamber, said chambers being substantially in the form of rectangular slots extending across said block and plate at right angles to the direction of relative motion thereof, means for sealing the ends of said chambers to prevent the flow of fluid therefrom, valve plate supports, means for securing said supports to said plate and said block, said supports Cit ports secured to said plate are deflected with respect to the ends thereof secured to said block, said supports be-' ing resilient in the direction of said relative movement and adapted thereby to exert a force on said plate and block tending to restore them to the null position.

20. In a valve construction, the combination of a valve block, a valve plate disposed with a first face thereof closely spaced from a face of said block, means supporting said plate for movement along said block, means securing said supporting means to said plate and said block, a cooperating land and chamber in said plate and block adapted to valve a fluid upon said movement of said plate, means adapted to introduce said fluid between said plate and block, whereby pressure of said fluid may urge them apart, said supporting means acting only in tension against'said pressure, a second face on said plate opposite said first plate face, a chamber formed in said second face, means forming a passageway between said first face and said chamber, a pressure plate closely spaced from said second face, means securing said pressure plate to said valve block, whereby pressure of said fluid between said plate and block is transmitted into said chamber in said second face to act between said pressure plate and valve plate, thereby to reduce said force urging said valve plate and block apart.

21. The combination defined in claim 9 in which said supporting means is non-extensible in the direction of said tension.

22. The combination defined in claim 20 in which said supporting means is adapted to yield to permit said movement of said plate alongsaid block.

References Cited in the file of this patent UNITED STATES PATENTS 263,809 Reaser Sept. 5, 1882 319,649 Wetherill June 9, 1885 375,144 Edward Dec. 20, 1887 621,460 Murphy Mar. 21, 1899 984,062 Berg Feb. 14, 1911 2,289,655 Kesling July 14, 1942 2,736,304 Thorner Feb. 28, 1956 2,737,165 Thorner Mar. 6, 1956 2,742,123 Exline Apr. 17, 1956 

